Counter mechanism, particularly for time totalizing systems and the like



FIG. 1

June 14, 1966 w, HAYDON ETAL 3,255,962

COUNTER MECHANISM, PARTICULARLY FOR TIME TOTALIZING SYSTEMS AND THE LIKE Filed June 10, 196-3 4 Sheets-Sheet 1 INVENTORS ARTHUR W. HAYDON WILLIAM D. RIGGS June 14, 1966 w. HAYDON ETAL 3,255,962

COUNTER MECHANISM, PARTICULARLY FOR TIME TOTALIZING SYSTEMS AND THE LIKE Filed June 10, 1965 4 Sheets-Sheet 2 FIG.

INVENTORS ARTHUR W. HAYDON WILLIAM D. RIGGS ATTORNE June 1966 A. w. HAYDON ETAL 3,255,962

COUNTER MECHANISM, PARTICULARLY FOR TIME TOTALIZING SYSTEMS AND THE LIKE Filed June 10, 1963 4 Sheets-Sheet 3 FIG. 3

INVENTORS ARTHUR W. HAYDON WILLIAM D. RIGGS ATTORNE Y5 June 14, 1966 A. w. HAYDON ETAL 3,255,962

COUNTER MECHANISM, PARTICULARLY FOR TIME TOTALIZING SYSTEMS AND THE LIKE 4 Sheets-Sheet 4 Filed June 10, 1963 FIG. 5

N 05 W3 G mwm w R E V W D J m N M )1 T Um E R l A W M WW 4 E B 3 n W S. o 2 l U J M 7 r I k United States Patent H of Connecticut Filed June 10, 1963, Ser. No. 286,640

9 Claims. (Cl. 235-91) The present invention relates generally to drum-type counters, and is directed more specifically to novel and advantageous structural features of a motor driven drum transfer counter.

In the copending application of Arthur W. Haydon, Serial No. 286,641, field June 10, 1963, there is described and claimed a novel system for recording the time useage of a large plurality of telephone circuits, for example. This system, referred to herein as atime totalizing system,,utilizes a large plurality of drum counters, each driven by a separate, synchronous motor and each arranged to be actuated by use of a partciular telephone circuit, whereby the total time usage of the particular circuit is recorded and indicated by the drum counter, which may be located at a. remote recording station. Periodically, a photograph is taken of the entire bank of counters of a specified group, to provide a photographic record from which more conventional accounting or billing records may be made. To avoid the possibility of any drum counter being in a transferring condition when a recording photograph is made, a special counter mechanism is employed comprising in general a counter of the type described and claimed in the Arthur W. Haydon Patent No. 3,069,083, granted December 18, 1962, in conjunction with a lost motion drive arrangement which accommodates completion of any transfer movement independently of the drive motor, once such movement has been commenced.

In a time totalizing system as above described, it is desirable in incorporate a large number of separately motordriven counters in a given panelstructure in view of the large numerical requirements of a complete system. In addition, the large numerical requirements dictate that the counter construction must be particularly rugged and reliable and, at the same time, capable of low cost manufacture and installation. Thus, it is the overall objective of the present invention to provide a motor driven drum counter integrated mechanism of highly compact, reliable and economical design and, at the same time, having the various operating and other characteristics required for use in the time totalizing system described above and forming the subject of the before-mentioned application of Arthur W. Haydon.

In view of the necessarily compact construction of a counter mechanism meeting the before-mentioned requirement, the individual, adjacent indicating drums necessarily are relatively narrow, which introduces special problems of effecting desired drum alignment and spacing. Accordingly, it is one of the specific aspects of the present invention to provide a drum transfer counter of the general type described and claimed in the before mentioned Arthur W. Haydon Patent No. 3,069,083, which incorporates novel and highly simplified arrangements for effecting predetermined, accurate alignment and spacing of the individual drums. The arrangement is such that, using parts of economically achievable dimensional tolerance,

reliably accurate spacing of the counter drums may be achieved to assure proper presentation of the numerical indicia on the drums in the recording or viewing windows of the counter housings. In one specific advantageous form of the mechanism, desired drum location is achieved through master spacing, from outside the drum Patented June 14, 1966 envelope, of motion compensating arms extending be-.

tween adjacent drums and otherwise required for effecting desired transfer motion of the drums. In another specific form of the invention a plurality of resilient, distortable nylon, Mylar or similar thermoplastic washers are applied over the drum shaft and received in machined spacing grooves therein between adjacent drums supported on the shaft. In the assembled counter, the washers are effectively fixed and serve 'to space the individaul counter drums accurately and effectively.

In accordance with another specific aspect of the invention, a novel drum counter mechanism is provided which includes a specifically advantageous. form of lost motion drive between the counting drums and the drive motor for the mechanism. Additionally, the novel lost motion drive arrangement includes a simplified spring clutch mechanism which enables the counter to be disengaged from the motor for proper setting of the counter during installation or during subsequent maintenance, for example.

In accordance with another specific aspect of the invention, an individually motor-driven counter mechanism is provided which includes a synchronous drive motor and a special, specifically novel arrangement for mounting the motor in operative arrangement with the counter mechanism. In particular, the motor mounting arrangement of the invention accommodates highly economical assembly, initially, of the complete mechanism and, in addition, accommodates'quick and economical replacement of the drive motor in the event of any malfunction.

A further specific aspect of the invention resides in the provision of specially designed drum counter mechanisms having. the various features above-mentioned and designed especially for use in a time totalizing system,

for example, which incorporates novel assembly-expediting features for simplified and economical mass production of the counter mechanisms. More particularly, the invention. provides a cam-compensated, planetary geardriven drum transfer counter in which the operatively related parts include special line-up openings arranged to be received over a special aligning element of'an as-. sembly jig. The arrangement is such that, during assembly of the component parts, all of the drums, planetary gears, etc., are properly aligned and enmeshed with complete reliability and great facility.

For a better understanding of the invention and a further discussion of'the above and other advantageous features thereof, reference should be made to the following detailed description and to the accompaning drawing in which:

FIG. 1 is a top plan view of a motor driven drum counter mechanism incorporating the various features of. the invention, with parts broken away to show certain details;

FIG. 2 is a cross-sectional view taken generally along line 22 of FIG. 1;

FIG. 3 is a cross-sectional view taken generally along line 3--3 of FIG. '1;

FIG. 4 is a fragmentary cross-sectional view similar to that of FIG. 2, with parts broken away to show details of the internal mechanism of the counter;

FIG. 5 is a cross-sectional'view taken generally along line 55 of FIG. 2; and

FIG. 6 is a fragmentary cross-sectional view taken generally along line 6-6 of FIG. 2 and illustrating a modified form of apparatus according to the invention.

Referring now to the drawing, the reference numerals 10, 11 designate spaced longitudinally disposed side plates of a U-shaped frame structure, the closed end of the U being broken away at the right in FIG. 1. In accordance with usual practice, the frame plates 10, 11 are secured in 3 spaced relation by a plurality of transfer spacer posts 12-14.

A shaft 15, descriptively referred to as the drum shaft, is supported at its end in the frame plates 10, 11 and rotatably supports a plurality of indicating drums 16-19 and an input element 20 in the form of a large gear.

As concerns its general operation, the counter mechanism, including the drums 16-19 and the input element 28, incorporates the inventive features of the Arthur W. Haydon Patent No. 3,069,083. Thus, the input element 20 and each of the indicating drums 16-19 advantageously is of molded plastic construction having a thin, disc-like web 21, and a cylindrical flange 22, and having formedthereon an output pinion 23, and a compensating cam 24. Each of the indicating drums 16-19 additionally has formed thereon an input gear 25 on the side of the web opposite the compensating cam and output pinion.

A -to-1 reduction drive between the input element and the lowest order indicating drum 16 and between each of the lower order indicating drums and the drum of the next higher order is provided by a planetary differential gear assembly 26, including a gear 27 and pinion 28. As indicated in FIG. 5, for example, the differential gear 27 meshes with the output pinion of a low order element, while the differential pinion 28 meshes with the input gear of the element of the next higher order, the input element 20 being, in effect, a low order element in the series.

To limit advancing movement of higher order drums to specific indexing periods (as when the indicating drum of the next lower order is advancing from its 9 to zero indicating position), compensating motion is imparted to the planetary differential gear assembly 26. This is accomplished by means of compensating arms 29 (FIGS. 2 and 4) which are pivoted outside the envelope of the indicating drums by a transversely disposed shaft 30 supported in the frame plates 10, 11. The compensating arms extend into the drum envelope between adjacent drums, and a cam follower wheel 31 mounted on each arm engages the outer surface of a compensating cam 24, the wheel 31 being urged into contact with the surface by means of a spring 32. The compensating arm 29 is connected to a radius arm 33 by means of a pin 34 advantageously disposed on the opposite side of the drum shaft 15 from the arm-supporting shaft 30. The radius arm 33, which is mounted on a hub 35 and rotatably journaled by a recessed bearing 36 in the higher order indicating. drum, carries a journal pin 37 upon which the differential gear assembly 26 is mounted.

As explained in greater detail in the before-mentioned Arthur W. Haydon patent, as a lower order drum rotates in an advancing direction from its zero indication to its 9 indication, and perhaps even slightly beyond, the compensating arm 29 is urged outward by the cam 24 of the lower order drum, such that the tendency of the difierential gear to advance the next higher order drum is exactly compensated for and canceled out by the retrogression of the differential gear as the compensating arm moves outward and pivots the radius arm 33. Eventually, when the lower order drum or element is between its 9 and zero positions, the surface of the compensating cam 24 changes from a slight outward incline (relative to the drum axis 15) to a sharp inward incline. Thus, during the final angular portion of a revolution of a low order element, the compensating arm 29 is caused to move inward toward the drum axis, causing an accumulated advance to be imparted to the next higher order drum, such that it is indexed through one-tenth of a revolution (in a ten-to-one ratio counter). By appropriate design of the compensating cam 24, the rotational arc encompassed by the sharp inwardly inclined portion, identified by the number 24a, may be kept to a minimum consistent with other design consideration (e.g., 30 degrees), such that indexing inputs to the higher order drums reliably occur only in the terminal portions of complete revolutions of lower order drums.

In accordance with the principles enunciated in the before-mentioned Arthur W. Haydon application directed to the time totalizing system, provision is made for driving the indicating drums 16-19 in such manner that, under no conditions, can a drum be stopped between index positions. To this end, the lowest order element of the series is a non-indicating input 20 which meshes with an input pinion 38. The input pinion 38 is, in turn, driven through a lost moton connection, including a first worm and worm gear set 39, 40 and a second worm and worm gear set 41, 42 from a synchronous drive motor 43. Suftficient lost motion is provided in the drive connection between the gears 38 and 40 to permit the input element 20 to be advanced in the forward direction under the spring-urged influence of the compensating arm 29, when the cam follower 31 is acting upon the sharply inclined portion 24a of the compensating cam 24. Accordingly, once the indexing or transfer movement commences, it will be completed even though the motor 43 may be stopped before the input element 20 actually has been gear-driven through the transfer portion of the cycle.

In accordance with one of the specific aspects of the invention, the lost motion drive input system includes the gears 38, 40 mounted for rotation on a shaft 44 anchored at one end to a forwardly extending arm 45 of an L-shaped mounting bracket 46 to be described subseqeuntly in more detail. The pinion 38 is received on the shaft 44, in aligned relation with the gear element 20, and is provided with a pair of rod-like abutment projections 47 which extend toward the gear 40 from diametrically opposed points on the gear 38. The gear 40 is positioned on the shaft 44 in alignment with the worm 39 and similarly has a pair of rod-like abutment projections 48 extending from diametrically opposed points on the gear 48 toward the gear 38.

As indicated particularly in FIGS. 1 and 3, thegears 38, 40, which advantageously are of molded plastic (e.g., nylon) construction, include cooperating hubs 49, 50 which serve to maintain a predetermined, spaced relation between the gears 38, 40, a spring 51 acting inward against the gear 40 to maintain the hubs 49, 50 in normal contact. The axial length of the bulbs 49, 50 is shorter by a predetermined amount than that of the rod-like projections 47, 48, so that the abutments overlap when thegear hubs are in contact. Accordingly, when the gears are in the positions shown in FIGS. 1 and 3, the a butment projections 47, 48, which lie substantially equal distances out from the shaft 44, are in interferring relation whereby the gear 38 will be driven forward through continued forward rotation of the worm gear 40. However, as indicated best in FIGS. 2 and 4, substantial circumferential clearance is provided between the forward extremities of the driven abutment elements 47 and the back extremities of the driving abutments 48 accommodating, in the illustrated mechanism, about degrees of free forward rotation of the gear 38. The arrangement is such that, even though the worm gear 40 remains locked in driving relation to the motor 43 through the worms 39, 41 and Worm gear 42, the input pinion 38 may advance independently under the influence of the compensating arm 29 and cam follower 31 on the inwardly inclined portion 24a of the compensating cam. As will be understood, the angle of free rotation required to be accommodated by the albutments 47, 48 is a function This enables the desirable only during the initial manufacturing stages, since in the contemplated utilization of the counter mechanism, resetting of the counter drums after installation is neither necessary nor desirable.

It is contemplated that the initial assembly of the mechanism will be such that the various counter drums are lined up at a very high number, permitting a limited, initial run-in of the mechanism by energization of the motor 43, to drive the counter forward to a zero position for test purposes. However, since it usually is impractical to devote such close attention to the counter as will insure stopping it exactly on zero during the test run-in, the described reset positions are extremely desirable for initially setting the counter drum slightly forward or backward to an all zero position. Actually, it is not necessary that the abutment elements 47, 48 be completely disengaged, if the worm gear 40 is shifted axially to such an extent as to be completely disengaged from the worm 39, which will accommodate free rotation of the stillengaged gears 38, 40.

As another advantageous, specific feature of the invention, the motor and input gear train unit advantageously is designed as a unitary sub-assembly, capable of separate installation in the complete mechanism and, more important, so designed as to accommodate free removal and replacement of the motor unit 43 in the event of operating difiiculty. As shown best in FIGS. 1 and 3, the motor-drive sub-assembly include-s the L- shaped bracket 46 which is formed by a transverse wall 52, extending between the frame plates 10, 11, and the forwardly extending arm 45, which is disposed immediately adjacent the frame 'plate 10. A pair of tab-like elements 53, 54 extend inward from upper and lower edges of the bracket arm 45, and these are arranged to engage and support a worm shaft 55 extending vertically in the assembly and journalling a molded element comprising the w-orm gear 42 and worm 39.

The transverse wall 52 of the L-shaped bracket 46 is provided with a central opening 56 (FIG. 1) in which is received a specially formed hub 57 of the motor 43.

Thus, the hub 57 comprises a locating bushing 58 arranged to be received snugly within the central opening 56, to position the motor 43 with respect thereto, an annular groove 59, and a front shoulder-forming flange 60. The overall hub structure desirably forms a journal bearing for a motor shaft 61 which carries the main drive worm 41 and, advantageously, the diameter of the drive worm 41 is less than that of the wall opening 56,

to accommodate the ready insertion of the assembled motor and drive worm through the opening.

The motor and worm sub-assembly 43, 41 is secured in place with effective rigidity by means of an arcuate, E-shaped snap ring 62, which is received in the annularly grooved portion 59 of the motor hub 57, being locked in position on the hub by the arms of the E and forcibly urging the motor forward into a predetermined seated position by reason of the arcuate or bowed contour of the snap ring. Thus, as indicated in FIG. 1, the center portion of the snap ring 62 acts axially forward against the hub shoulder 60, while the side edges of the ring act rearward against the front surface of the bracket wall 52. The arrangement is such that the motor and worm subassembly is firmly secured in place on the L-shaped bracket 46. However, in the event it becomes desirable or expedient to replace the motor 43 for any reason, the old one may be removed quickly by simply withdrawing the snap ring 62 and withdrawing the motor .and worm sub-assembly rearward. In this respect, it is specifically contemplated that the closed end of the -U-shaped bracket will be spaced sufficiently far from the transverse bracket wall 52 as to accommodate rearward withdrawal of the motor and worm 41 Without disassembly of the U- shaped frame or the L-shaped bracket 46. The new motor maybe replaced by insertion of its worm 41 and hub 57 through the opening 56 and replacement of the snap ring 62. It will be understood, this is an extremely advantageous assembly arrangement, not only for. the

realization of economy in manufacture, but, perhaps more importantly, from the standpoint of maintenance of a large number of mechanisms where occasional replacement of a motor may be required.

Advantageously, the entire sub-assembled bracket 46 with its mounted motor and drive gears is secured in the U-shaped frame by means of outwardly extending tabs 63 on the bracket plate 52 which are received in corresponding openings 64 in the frame plates 10, 11. Thus, the complete power train may be sub-assembled independently and incorporated in the complete device with great facility. In accordance with another specific aspect of the in- -vention, specifically novel arrangements are provided for desirably spacing the individual counter drums 16-19 and the input gear element 20, such that the individual drums are desirably aligned in the final assembly for proper viewing through a window 65 in a housing or cover element 66 which is slidably received over the exterior of the assembly, and encloses the assembly, at least to the extent of providing top and bottom cover walls 67, 68 extending back to the transverse bracket wall 52 and serving in conjunction with the side frame plates 10, 11 substantially to enclose the counter mechanism and its drive trains.

Since the individual drum elements 1619 and the lower order gear element 20 are, advantageously, of molded plastic construction, and the mechanism, in general, is designed for economical mass production, it is impractical in most cases to so maintain the axial tolerances of the drums that a cumulative axial dimensional error of undesirable proportions will not be introduced, at least in the occasional unit. Thus, the mechanism of the invention includes a simplified mechanical arrangement by which the spacing of the molded plastic elements 1620 may be controlled or determined by the tolerances of machined, steel parts.

Specifically, in the first illustrated form of the invention, spacing of the elements 1620 is effected through an advantageous use of the compensating arms 29, with machined metal elements being provided, in turn, to effect reliably accurate spacing of the compensating arms. Thus, as shown in FIG. 1, each of the compensating arms 29 is mounted on a special bushing 69 having a peenedover end 70 and a shoulder 71 serving to locate the associated compensating arm, the entire sub-assembly being pivoted on the transverse shaft 30.

The metal bushing elements 69, which may be turned out on a screw machine, for example, with substantial precision and at low cost, are sub-assembled with the compensating arms 29 and then applied over the shaft 30 during assembly of the unit. The compensating arm located between the drum elements 18, 19 is spaced from the frame plate 11 by its bushing 69, and each lower order compensating arm is spaced from the next arm by its attached bushing, as will be understood. At the low order end of the mechanism, a spring 72 advantageously is positioned to act between the frame plate 10 and the bushing 69 of the lowest order compensating arm, to urge the entire stack of special bushings toward the frame plate 11 and thus maintain them in the desired contacting or spacing relation.

Using the established spacing of the compensating arms 29, location of the elements along the shaft 15 is provided by means of a rounded head portion 73 (FIG. 5) of the stub shaft 74 by which each cam follower 31 is secured to its compensating arm 29. Thus, the rounded shaft head 73 is arranged to project axially beyond the cam fo1- lower 31 and is adapted to bear against the lefthand facing surfaces (FIG. 5) of the drum elements 1618 and the gear element 20 to limit the leftward movement of those elements.

In order to reference the rightward facing surfaces of the elements 16-19 to the pre-spaced compensating arms 29, advantageous use is made of the bushings 35 on which the radius arms 33 are secured. Thus, each radius arm is spaced from its associated compensating arm 29 by aspacing shoulder 75 (FIG. 6) on a connecting pin 34, which is interposed between the compensating arm 29 and the radius arm 33. The bushings 35, as shown in FIG. 5, are provided with bearing surfaces '76 having axial contact with rightward facing surfaces of the drum elements 16-19. Thus, tendency for the drums to move to the right is limited by the bushings 35, acting through the pre-positioned compensating arms 29. Alternatively, or in addition, the connecting pins 34 may be provided with extensions 34a projecting to the left (FIG. 6) and having rounded end surfaces for spacing engagement with the right hand facing surfaces of the drum elements 16-19.

Advantageously, the drum spacing established by the compensating arms 29, as described, is relatively loose, so that each of the drums rotates freely. However, since the cumulative spacing errors are limited by accurate machining of the bushings 69, substantial dimensional latitude is provided in the molding of the individual drum elements 16-19 and the gear element 20, such that the elements may be manufactured on an economical basis.

In the modified embodiment of FIG. 6, even more precise drum positioning is effected by machining a plurality of special grooves 116 in the drum shaft 115. Ad-

vantageously, the spceial grooves are positioned on each side of each of the elements 16-20, as suggested by the fragmentary view of FIG. 6. Cooperating with the special grooves 116 are spacing washers 117 formed of a somewhat resilient material, most advantageously nylon plastic. The spacing washers have central openings slightly smaller than the principal diameter of the drum shaft 115, so as to be effectively seated in the spacing groove when applied over the shaft.

During the assembly of the mechanism of FIG. 6, the application of each drum element over the shaft 115 is preceded and followed by the sliding of a nylon spacing washer 117 over the shaft to be snapped into place in the appropriate spacing groove 116. Thus, in the final assembly, each element of the counter mechanism is spaced with high accuracy by a confining pair of spacing washers 117. The last described system is, of course, effectively free of cumulative spacing error and, since the spacing control is more direct, constitutes a more reliably accurate assembly. However, the arrangement of FIGS.- 1-5 may be preferred because of its greater ease of assembly.

The separate arrangements (spacing shoulder 75 and rounded extension 34a, and the nylon washers 117) illustrated in FIG. 6 for spacing indicating drum elements normally are used in the alternative. However, these arrangements are not mutually exclusive, and both arrangements are employed in the embodiment of FIG. 6 to provide extremely effective spacing of the drums.

In assembling the motor driven mechanism of the invention, the input gear element 20 must be properly connected to the succession of higher order elements 16-19, each through the intermediary of a differential planetary gear mechanism. Accordingly, special effort must be made to effect proper alignment and meshing of the various parts, to make certain, for example, that an adjacent set of counter drums is not improperly engaged by the amount of, say, one gear tooth. To this end, the mechanism of the invention incorporates operative components adapted especially to be received on an assembly alignment jig of simple design, such that precise, proper alignment and meshing engagement of all elements of the assembly is reliably and automatically assured as the assembly progresses. Thus, in accordance with the invention, each of the drum elements 16- 19, the gear element 20, and each of the differential gear assemblies 26 is provided with an alignment opening 77, 78 or 79, as shown in FIG. 5. In addition, the frame plates 10, 11 are provided with predetermined, opposed alignment openings 80, 81. All of the aforementioned alignment openings are so located in the respective elements that, when they are disposed along a predetermined alignment axis, the drum elements 16-19, and input gear element 20 will be operatively related, properly meshed with the differential gear assemblies 26, and, advantageously, positioned to indicate a high registration number.

In conjunction with the various alignment holes, a novel alignment jig is provided, which consists, principally, of a fiat base plate 83, an elongated, vertically disposed (in operating position) alignment rod 84 and a locating bar 85. When the assembly operation is commenced, the frame plate 11, forming one part of an advantageously two-part, U-shaped, frame structure, is placed upon the assembly jig in such a way that the opening 81 is received over the alignment rod 84, and an opening 86 is received over the locating bar 85, thereby fixing the position of the frame plate 11 relative to the assembly jig. With the drum shaft 15 properly received in the frame plate 11 and projecting upward therefrom, the highest order drum element 19 (preceded, if desired, by an appropriate spacing washer) is applied over both the drum shaft 15 and the alignment rod 84, so as to have a predetermined, precise rotational orientationrelative to the frame plate 11. Thereafter, an assembly comprising a bushing 35, radius arm 33 and differential gear assembly 26 is applied over the drum shaft 15 and drum hub 36, with the alignment rod 84 being received in the opening 79 in the differential gear. During this assembly operation, the rotational orientation of the differential gear is properly fixed for meshing with the high order drum 19 and for the next lower order drum 18, and the rotational orientation of the radius arms 33 also is properly determined. The subsequently assembled compensating arm 29 automatically is. properly positioned upon its reception over the supporting shaft 30 and its connection to the pin 34.

As will be understood, the assembly proceeds in sequence along the lines above described, with each operatively associated part being precisely orientated relative to all of the other parts, by virtue of the locating rod 84 and the various locating or alignment openings 77- 81. This arrangement remarkably increases the efficiency of assembly of the unit, and, of particular importance, prevents slight (e.-g., one gear tooth) misalignments which might otherwise go undetected during assembly.

The motor driven counter assembly of the invention, being particularly adapted for incorporation in the time totalizing system of the before-mentioned copending Arthur W.. Haydon application, Serial No. 286,641, is especially advantageous in its specific, structural makeup, which enables the unit to be manufactured in great quantity on an economical basis, reliably assembled, and easily and quickly serviced. At the same time, the unit is of a highly compact construction suitable for incorporation in a large bank of counters, as is contemplated in the time totalizing system.

One of the specific features of the invention resides in the described, highly simplified, gear arrangement for providing a 10st motion drive between a motor and worm gear input and a non-indicating low order element, according to the broader principles of the before-mentioned Arthur W. Haydon application. The illustrated lost motion drive arrangement, including gears 38, 40, is simple, economical and wholly effective and, in addition, incorporates a simple disengaging or clutching feature, which enables the counter to be advanced or retracted during assembly to a position of all zeros. In this respect, it is contemplated to initially assemble the counter drums through the before-described alignment jig at an 8-8-8-8 position, for example, subsequent to which, the assembled device is actuated by energization of its motor 43 for a short test run-in of the mechanism. Desirably, the test run-in of the mechanism would advance the counter drums to an all-zeroposition, but

this easily can be missed by momentary operator inat- I tention, for example, in which case the disengage feature enables the counter to be reset to zero.

Another particularly advantageous feature of the invention, resides in the unitary highly simplified drive assembly, including an L-shaped bracket mounting a worm gear drive train and having an opening for receiving and locating a forward shaft bushing of a small drive motor. In accordance with the invention, the bushing is so arranged that a bowed, E-shaped, snap ring can be applied thereto in its assembled position, to lock the motor in fixed relation in the assembly. Thus, the motor unit itself, which advantageously may be as the type shown for example in the Riggs US. Patent No. 3,014,141, or the Van Lieshout, et al., US. Patent No. 2,981,855, may be quickly and expeditiously removed and replaced, as may be required from time to time for maintenance of a large bank of motor driven counter units.

A more specific feature of the invention resides in a simplified and wholly elfective arrangement, intended specifically for a compact counter mechanism using molded plastic indicator drum elements, for properly spacing the elements in an assembly. Thus, simplified provisions are made for avoiding cumulative axial error in drum dimensions without adding significantly to the cost of the assembly or the complexity of its manufacture. In one such advantageous arrangement, the several drums are spaced by special compensating arms, anchored outside the drum envelope. In another advantageous arrangement, individual snapped-in-place nylon spacing washers locate the indicating drums in the desired manner.

The invention also incorporates specifically novel and advantageous arrangements for automatically and reliably aligning all operative, interrelated parts of the mechanism during assembly, greatly minimizing the attention required of the assembling personnel and also effectively avoiding slight misalignments of the gear-connected parts which might easily go undetected during the assembly stages.

As will be understood, the specific mechanism herein illustrated and described may be modified in various respects without departing from the clear teachings of the disclosure. Accordingly, reference should be made to the following appended claims in determining the full scope of the invention.

What is claimed is:

1. In a transfer counter,

(a) a counter assembly having a plurality of interconnected counter elements including a lower order element and a higher order element,

(b) drive means connected to said lower order element for operating the same,

(c) lost motion means for permitting relative motion between said lower order element and said drive means,

(d) means for continuing the operation of said lower order element independently of said drive means until said lower order element reaches a predetermined position, and

(e) reset means operatively associated with said lost motion means for disengaging said drive means from said lower order element, to enable the resetting of said counter to a reference position, said reset means including a pair of coaxially mounted gears which are adjustable for enabling said resetting of said counter.

2. In a transfer counter,

(a) a counter assembly having a plurality of interconnected counter elements including a lower order element and a higher order element, each of said counter elements having predetermined index positions,

(b) drive means forming an input to said counter assembly for operating said counter elements,

(c) lost motion means for permitting relative motion between said counter elements and said drive means, said lost motion means including a pair of gears respectively connected to said drive means and said lower order element, said gears being coaxially mounted and independently rotatable with respect to each other, and means separate from said lost motion means and effective during a time when at least one of said counter elements is in .a position intermediate its predetermined index positions for continuing the operation of said one counter element independently of said drive means until said one element reaches a predetermined index position.

3. In a transfer counter,

(a) a counter assembly having .a plurality of counter elements including a lower order element and a higher order element,

(b) drive means connected to said lower order element for operating the same,

(c) transfer means interconnecting said lower order element with said higher order element for operating said higher order element during a selected portion of the operation of said lower order element and in predetermined relationship therewith, and

(d) lost motion means for permitting relative motion between said lower order element and said drive means, said lost motion means including a pair of gears respectively connected to said drive means and said lower order element,

(e) said transfer means acting on said lower order element unrestricted by said drive means to continue the operation ofsaid lower order element independently of said drive means until said lower order element reaches a predetermined position.

4. In a transfer counter,

(a) a counter assembly having a plurality of counter elements including a lower order element and a higher order element,

(b) drive means connected to said lower order element for operating the same,

(0) resiliently biased transfer means interconnecting said lower order element with said higher order element for rapidly operating said higher order element only during a selected portion of the operation of said lower order element and in predetermined relationship therewith, and

' (d) lost motion means effective during'operation of said higher order element for permitting relative motion between said lower order element and said drive means, said lost motion means including a pair of gears respectively connected to said drive means and said lower order element,

(e) the resilient bias of said transfer means acting on said lower order element to continue the operation thereof independently of said drive means until said lower order element reaches a predetermined position. I

5. In a transfer counter.

(a) a counter assembly having a plurality of counter elements including a lower order element and a higher order element, each of said counter elements having predetermined index positions,

(b) non-reversible drive means connected to said lower order element for operating the same,

(c) resiliently biased transfer means interconnecting said lower order element with said higher order element for operating said higher order element during a selected portion of the operation of said lower order element and in predetermined relationship therewith,

(d) lost motion means for permitting relative motion between said lower order element and said drive means, said lost motion means including a pair of gears respectively connected to said drive means and said lower order element,

(e) said transfer means acting on said lower order element during a time when said lower order element is in a position intermediate its predetermined index positions to continue the operation of said lower order element independently of said drive means until said lower order element reaches a predetermined index position, and

(f) means operatively associated with said lost motion means for disengaging said drive means and said lower order element, to enable the resetting of said counter to a reference position.

6. In a transfer counter,

(a) a counter assembly having a plurality of counter elements including a lower order element and a higher order element, each of said counter elements? having predetermined index positions,

' (b) drive means connected to said lower order element for operating the same, said drive means including a unidirectional motor and gear means interposed between said motor and said lower order element,

() resiliently biased transfer means interconnecting said lower order element with said higher order element for rapidly operating said higher order element only during a selected portion of the operation of said lower order element and in predetermined relationship therewith,

(d) lost motion means for permitting relative motion between said lower order element and said motor and including first and second sets of interfering lugs, said first set of lugs being movable with said motor and said second set of lugs being movable with said gear means,

(e) said transfer means acting on said lower order element during a time when said lower order element is in a position intermediate its predetermined index positions to continue the operation of said lower order element independently of said motor until said lower order element reaches one of its predetermined index positions, and

(f) reset means including a pair of coaxially mounted gears operatively associated with said lost motion means, said gears being adjustable to enable the resetting of said counter to a reference position.

7. A counter and drive mechanism comprising (a) a counter assembly having a plurality of interconnected counter elements driven by a low order counter element,

('b) non-reversibly operable drive means forming a drive input to said low order counter element,

(c) said drive means including a worm and worm gear assembly and a drive gear coaxially mounted and independently rotatable with respect to said Worm gear, said drive gear being maintained in driving relation with said low order counter element,

((1) means for transmitting driving power between said worm gear and said drive gear and for'permitting relative motion therebetween,

(e) means mounting said worm and worm gear for movement into and out of meshing relation, and (f) resilient means urging said worm and worm gear into said meshing relation,

(g) said worm and worm gear being selectively movable out of meshing relation to accommodate setting of said counter elements.

S. A counter and drive mechanism comprising (-a) a counter assembly having a plurality of interconnected counter elements driven by a low order counter element,

(b) non-reversibly operable drive means forming a drive input to said low order counter element,

(c) said drive means including a worm and worm gear assembly and a drive gear normally connected to said worm gear,

((1) said worm gear and said drive gear being coaxially mounted and independently rotatable,

(e) said worm gear and said drive gear being drivingly engaged by interfering lugs,

(f) said worm gear and said drive gear being slidably separable to disengage said interfering lugs and accommodate free relative rotation between said worm gear and said drive gear,

(g) means mounting said worm and said worm gear for movement into and out of meshing relation, and

(h) resilient means urging said worm and said worm gear into said meshing relation,

(i) said worm and said worm gear being selectively movable out of meshing relation to accommodate setting of said counter elements.

9. The mechanism of claim 8, in which (a) said counter is mounted in a frame structure comprising, in substance, a pair of side frame plates forming closed sides and having at least one open side,

(b) said worm gear and drive gear being mounted on an axis perpendicular to said side frame plates and' lying closely adjacent said open side,

(0) said worm gear and drive gear being readily accessible through said open side for effecting disengagement thereof.

References Cited by the Examiner UNITED STATES PATENTS 300,959 6/1884 Doncel 19267 655,973 8/1900 Hakewessell et al. 19267 X 1,163,170 12/1915 Pearson 192--67 1,690,356 11/1928 Zubaty 235-96 X 1,919,511 7/1933 Helgeby 235-144 2,365,510 12/1944 Barnes 23591 2,456,101 12/1948 Yeasting 235l36 2,490,725 12/1949 Yeasting 235-136 2,578,358 12/1951 Jellison 235132 X 2,679,357 5/1954 Rosenberger 235-91 2,916,569 12/1959 Fackler et a1 235-103 X 2,919,912 1/ 1960 Brinkhaus 269-47 2,952,282 9/1960 McHenry 269-47 3,069,083 1 2/1962 Haydon 235--136 3,072,330 1/1963 OCoine et a1. 23591 3,123,293 3/1964 Kernander et a1. 23591 X 3,128,041 4/1964 Adler 235-91 LEO SMILOW, Primary Examiner.

C. G. COVELL, Examiner. 

8. A COUNTER AND DRIVE MECHANISM COMPRISING (A) A COUNTER ASSEMBLY HAVING A PLURALITY OF INTERCONNECTED COUNTER ELEMENTS DRIVEN BY A LOW ORDER COUNTER ELEMENT, (B) NON-REVERSIBLY OPERABLE DRIVE MEANS FORMING A DRIVE INPUT TO SAID LOW ORDER COUNTER ELEMENT, (C) SAID DRIVE MEANS INCLUDING A WORM AND WORM GEAR ASSEMBLY AND A DRIVE GEAR NORMALLY CONNECTED TO SAID WORM GEAR, (D) SAID WORM GEAR AND SAID DRIVE GEAR BEING COAXIALLY MOUNTED AND INDEPENDENTLY ROTATABLE, (E) SAID WORM GEAR AND SAID DRIVE GEAR BEING DRIVINGLY ENGAGED BY INTERFERING LUGS, (F) SAID WORM GEAR AND SAID DRIVE GEAR BEING SLIDABLY SEPARABLE TO DISENGAGE SAID INTERFERING LUGS AND ACCOMMODATE FREE RELATIVE ROTATION BETWEEN SAID WORM GEAR AND SAID DRIVE GEAR, (G) MEANS MOUNTING SAID WORM AND SAID WORM GEAR FOR MOVEMENT INTO AND OUT OF MESHING RELATION, AND (H) RESILIENT MEANS URGING SAID WORM AND SAID WORM GEAR INTO SAID MESHING RELATION, (I) SAID WORM AND SAID WORM GEAR BEING SELECTIVELY MOVABLE OUT OF MESHING RELATION TO ACCOMMODATE SETTING OF SAID COUNTER ELEMENTS. 